WO2002016802A1 - Transmission pour un changement de vitesse a variation continue fiable par engrenement et dispositif de transmission a variation continue pour vehicules automobiles utilisant cette transmission - Google Patents

Transmission pour un changement de vitesse a variation continue fiable par engrenement et dispositif de transmission a variation continue pour vehicules automobiles utilisant cette transmission Download PDF

Info

Publication number
WO2002016802A1
WO2002016802A1 PCT/KR2001/001421 KR0101421W WO0216802A1 WO 2002016802 A1 WO2002016802 A1 WO 2002016802A1 KR 0101421 W KR0101421 W KR 0101421W WO 0216802 A1 WO0216802 A1 WO 0216802A1
Authority
WO
WIPO (PCT)
Prior art keywords
variable transmission
output
continuously variable
vehicle
teeth
Prior art date
Application number
PCT/KR2001/001421
Other languages
English (en)
Japanese (ja)
Inventor
Teak-Seo Goo
Original Assignee
Goo Teak Seo
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Goo Teak Seo filed Critical Goo Teak Seo
Priority to US10/111,239 priority Critical patent/US6645106B2/en
Priority to AU2001282633A priority patent/AU2001282633A1/en
Publication of WO2002016802A1 publication Critical patent/WO2002016802A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
    • F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
    • F16H3/56—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears both central gears being sun gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously

Definitions

  • TECHNICAL FIELD The present invention minimizes power loss and achieves a reliable continuously variable transmission operation through a gear combination while minimizing power loss.
  • TECHNICAL FIELD The present invention relates to a continuously variable transmission for a vehicle, which uses a combination of a transmission to be executed and a gear thereof, and provides an optimal speed ratio to an engine output in a continuously variable manner using the transmission. 2. Description of the Related Art Various types of continuously variable transmissions have been proposed so far, and are roughly classified into mechanical, electric, and hydraulic types.
  • FIG. 1 is a schematic diagram for explaining a planetary gear combination system of a transmission according to the present invention.
  • FIG. 2A to FIG. 2F are explanatory diagrams of the shift principle of the continuously variable transmission according to the present invention.
  • FIG. 3 shows that the continuously variable transmission for a vehicle according to the present invention includes a known power generation device, a hydraulic pressure generating and providing device, a wheel driving device for driving wheels, and an electronic device including a first half operating portion of the vehicle.
  • FIG. 1 is a configuration example of an embodiment for explaining a connection and an operation state of other known components with a known vehicle including an electronic control device for performing control.
  • FIG. 4 is a comparison diagram of the operating characteristics of a conventional five-speed transmission and the continuously variable transmission of the present invention.
  • BEST MODE FOR CARRYING OUT THE INVENTION A continuously variable transmission according to the present invention outputs a main driving force applied to an input stage while continuously changing the speed, but in particular, a reliable continuously variable transmission operation through a gear combination.
  • Carrier means connected to the input stage shaft and revolving while carrying a large number of planetary gear sets, and assembling so as to freely rotate while being supported by the carrier means.
  • the first output means which is coupled to the outer side of the arrangement of the planetary gears (S2) having the larger number of teeth to provide the transmitted rotational force to the output stage shaft; Of the planetary gear (S2) toward A second output means coupled to the inside of the planetary gears (S1) having the smaller number of teeth, the second output means being adapted to provide the rotational force received and transmitted to the output stage shaft; And a speed change means for changing the rotation speed while rotating in the same direction as the speed change means.
  • the connection between the input stage shaft and the carrier means is connected by a soup line.
  • the first output means includes a ring gear which is coupled to the outside of the arrangement of the planetary gears (S2) having a large number of teeth and rotates, and a forward clutch which closes a connection between the ring gear and the output stage shaft.
  • the second output means includes a reverse sun gear that is engaged inside the arrangement of the planetary gears (S2) having a large number of teeth and rotates, and a reverse clutch that controls the connection between the reverse sun gear and the drive shaft of the output stage.
  • the above shifter The gear stage is connected to the inside of the arrangement of the planetary gears (S1) having a small number of teeth, and the transmission sun gear is rotated, and the hydraulic pressure that provides power so that the transmission sun gear rotates in the same direction as the carrier means or maintains a stopped state. Including motor.
  • the transmission means When the continuously variable transmission transmits torque through the first output means, the transmission means provides power through the hydraulic motor so that the transmission sun gear rotates in the same direction as the carrier means.
  • the hydraulic motor When the torque is transmitted through the second output means so that the speed is continuously variable between the input / output stages due to the change, the hydraulic motor is stopped and the transmission sun gear is kept stopped. In this way, a fixed speed change is performed between the input / output stages by the number of gear teeth, and particularly when the rotational force is transmitted to the first output means, the main drive rotational force provided through the input stage shaft And the auxiliary driving torque provided through the hydraulic motor is combined through a speed change process to be applied to the output stage shaft.
  • the variable speed sun gear is a rotary power generated in a carrier rotational direction when a number of planetary gear sets transmit rotational force to the ring gear while revolving and revolving around the variable speed sun gear as a central axis. Since the structure is driven by the sub-drive torque provided by the hydraulic motor, the sub-drive torque is relatively small compared to the main drive torque, and the power is sufficient.
  • a continuously variable transmission for a vehicle includes a known power generation device, a hydraulic pressure forming and providing device, a wheel driving device for driving wheels, and an operating part in the first half of the vehicle.
  • a continuously variable transmission for a vehicle for outputting a rotational force input from the power generating device to the wheel drive device while continuously changing the rotational force input from the power generating device.
  • a carrier means connected to the turbine shaft of the power generation device for rotating (revolving) a large number of planetary gear sets in a trivial manner, and assembled so as to freely rotate while being supported by the carrier means.
  • First output means positive rotation output
  • the second output means reverse rotation output
  • a speed change means for performing a speed change operation while rotating in the same direction as the carrier means.
  • a gear combination method of a transmission relates to a gear combination method of a transmission for outputting a main driving torque applied to an input stage shaft to an output stage shaft while continuously changing the speed.
  • the input stage shaft is connected to a carrier means for rotating (revolving) a number of planetary gear sets without pinching, so that the number of teeth of one side planetary gear (S1) of each planetary gear set integrally formed is different.
  • Side planetary gear (S2) teeth A large number of planetary gear sets (Sl, S2) formed so as to be relatively smaller than the number are assembled so as to freely rotate while being supported by the above-mentioned carrier means, and the above-mentioned planetary gears having more teeth are assembled.
  • the transmitted torque positive rotation output
  • the reverse sun gear is assembled inside the arrangement of the planetary gears (S2) to provide the transmitted rotational force (reverse rotation output) to the output stage shaft, so that the number of teeth is smaller.
  • the gearshift sun gear is assembled inside the arrangement of the planetary gears (S1), the gearshift sun gear provides an auxiliary driving torque so as to perform gearshifting operations while rotating in the same direction as the carrier. It is especially important to do so.
  • FIG. 1 is a schematic diagram illustrating a gear combination system of a transmission according to the present invention.
  • the planetary gear combination system of the continuously variable transmission of the present invention is a conventional Ravigneaux Gears system or a Simpson Gears system, which is completely different from the conventional one. Is simply referred to as “GTS gear union system”.
  • a carrier connected to a turbine shaft (2) by a soup line is provided, and a set of planetary gears (6) supported by the carrier is provided.
  • a set of planetary gears is integrally provided at both ends of multiple shafts, and one shaft has a planetary gear (S2) with many teeth on one side and a planetary gear with few teeth on the other side. (S1) is provided.
  • a sun gear (Al, 7) is combined with a ring gear (5) on the outside of the planetary gears (S2, 6) and a reverse sun gear (A2, 8) on the inside, and a gear shift sun gear (Al, 7) on the inside of the planetary gears (Sl, 6).
  • the outside of the transmission sun gear shaft is connected to a hydraulic motor (9) by a soup line and driven by the hydraulic motor to perform a transmission function while rotating separately from the input shaft.
  • the turbine shaft (2) rotates
  • the planetary gears (S1, S2) (6) rotate and revolve around the variable speed sun gear (Al, 7) around the central axis (the reverse sun gear (A2, 8) rotates freely).
  • a predetermined forward speed increase ratio is output, and by driving the hydraulic motor (9) to gradually rotate the shifting sun gear, the above speed increase output ratio changes. If the speed change machining is performed and the speed of the transmission sun gear is increased or decreased, the reduction ratio increases or decreases, and if the speed of the transmission sun gear is fixed and the speed of the turbine shaft is increased or decreased, A double continuously variable transmission operation in which the speed increase ratio increases or decreases is performed.
  • the turbine shaft (2) causes the planetary gears (Sl, S2) to center on the shifting sun gear.
  • the reverse sun gear (A2, 8) is rotated while rotating and revolving on the shaft, and a predetermined reverse rotation reduction ratio is output, and the reduction gear is operated with a fixed reduction ratio.
  • the main drive turbine shaft (2) functions to transmit the rotational force resulting from the shift to the driven shaft by distributing the rotational force of the input shaft, and the sub-drive transmission sun gear (Al, 7) functions as a transmission. This is characterized in that power loss is minimized by allowing the combined output to be output to the main drive during the speed change processing of the sub-drive speed change sun gear.
  • the rotating sun gear when the carrier rotates and the planetary gear rotates and revolves and transmits the rotating force that has been shifted, the rotating sun gear generates rotational force in the same direction, and the input power is approximately 1/150 of the input power.
  • the feature is that the rotation of the variable speed sun gear can be controlled with relatively small driving force.
  • gears are based on the mouth ring contact movement of the pitch source, and the change in the rotation angle at the time of contact between the two gears can be expressed by the following equation.
  • M is a module
  • Zi and 2 are the number of teeth, and is also the pitch source
  • ⁇ is the angular velocity
  • ⁇ is the rotational speed
  • / is the gear ratio
  • a is the sun gear
  • b is the Planet gears
  • c represents a ring gear
  • s represents a carrier.
  • Figure 2 ⁇ shows a case where the sun gear is fixed and the carrier is rotated. Therefore, these contact points correspond to the pitch points.
  • No. Fig. 2C shows the case where the sun gear is rotated with the carrier fixed. Points A, B, C, and D are initially aligned on a straight line and if the sun gear rotates about 0a, the rotation angle of the planetary gear will be 0b. Is as follows.
  • Fig. 2D shows the case where the carrier and sun gear rotate simultaneously (the carrier and sun gear have different rotation speeds at this time). If the two movements of Fig. 2B and Fig. 2C are overlapped, is there. If the carrier and the sun gear are rotated by 0 s and 0 a, respectively, the rotation angle of the ring gear is as follows.
  • the reduction ratio when the speed of the variable speed sun gear increases by lrpm increases by 0.004, and the speed increase ratio when the rotation speed of the turbine shaft carrier increases by lrpm increases by 0.006.
  • the torque on the input side is distributed to the main drive turbine shaft and sub-drive, and after performing other functions, they are combined and output to the output shaft with little power loss.
  • the power required was assembled on the main drive turbine shaft.
  • the drive can be sufficiently performed with 1/150 power and the rotational force generated in the shifting sun gear is generated in proportion to the input power.
  • the shift control for very large power with small power becomes possible, and the sub-drive hydraulic motor is installed inside the transmission and driven by receiving hydraulic pressure with an oil pump that supplies hydraulic pressure and lubricating oil.
  • the rotation speed is controlled by controlling the flow rate of the subpulp, and the subpulp is controlled by the signal of the controller (TCU).
  • Figures 2E and 2F show a reverse rotation deceleration system in which the planetary gears (Sl, S2) (6) of the turbine shaft rotate and revolve around the variable speed sun gear (7) (the ring gear rotates freely).
  • the process of operating the reverse sun gear (8) in reverse rotation and decelerating to perform the fixed deceleration function as a reverse device is expressed as follows.
  • the gear combination method of the transmission according to the present invention is clearly different from the conventionally known gear combination method.
  • the planetary gear unit union system that has been widely used until now is the lavigne one-gear system.
  • the Simpson gear system is composed of a pair of planetary gears and ring gears in which one sun gear is installed as a long gear and has a small number of teeth, and a pair of planetary gears and ring gears with a large number of teeth.
  • One sun gear and two sets of planet gears and two A clutch and a brake are installed on each gear shaft, and the 4th to 5th clutches are tightened sequentially with a gear with a large reduction ratio and a gear with a small reduction ratio (ON-
  • the conventional two methods are all transmissions with a gear (step).
  • the gear combination system of the continuously variable transmission has a structure in which the planetary gears (Sl, S2) (6) each having a different number of teeth (gears) are integrally provided on the shaft and the number of teeth is large.
  • the reverse sun gear (8) with a small number of teeth is combined with the ring gear (5) of positive rotation output on the outside of the gear (S2), and the planetary gear (S1) with a small number of teeth on the other side.
  • a transmission sun gear (7) is coupled to the inside, and a hydraulic motor (9) of auxiliary driving means is provided on the transmission sun gear shaft to control the rotation speed of the transmission sun gear, so that the planetary gears apply rotational force to the ring gear.
  • the transmission is to be performed continuously by increasing or decreasing the speed of the sun gear when transmitting.
  • the gear combination system for continuously variable transmission is such that the ring gear (5) and the other planetary gears (Sl, S2) (6) each having the same number of teeth are integrated on the same shaft.
  • the main drive torque transmission function is performed by distributing the torque of the input shaft, and the sub-drive torque distributed to the hydraulic motor (9) is reduced. Since the power is combined with the above-mentioned main driving torque during the speed changing process and appears as one output, the power for rotating the sub-driving sun gear is not substantially consumed. It has the following characteristics.
  • the transmission gear combination system for the power transmission device is a unique gear system that operates better than the conventional gear combination system Ravigneaux Gears and Simpson Gears described above. It is a gear thread combination system.
  • FIG. 3 shows a continuously variable transmission for a vehicle according to the present invention, which includes a known power generation device, a hydraulic pressure forming and providing device, a wheel driving device for driving wheels, and a first half operating portion of the vehicle.
  • FIG. 1 is a configuration example of an embodiment for explaining a connection and an operation state of a known vehicle provided with an electronic control device for controlling a vehicle and other components.
  • 1 is a torque converter
  • 2 is a turbine shaft for providing the main driving torque
  • 3 is a forward clutch
  • 4 is a reverse clutch
  • 5 is a ring gear
  • 6 is a planetary gear set
  • 7 is a speed change Sun gear
  • 8 is a reverse sun gear
  • 9 is a hydraulic motor for providing auxiliary driving torque to the above-mentioned shifting sun gear
  • 10 is an oil pump shaft
  • 11 is an oil pump
  • 12 is a sabo valve (electronic proportional flow control pulp)
  • 13 is a difference Dynamic gear
  • 14 is a check valve
  • 15 is an akiyumu
  • 16 is Mayuaru pulp
  • 17 is a regulator
  • 18 is a relief pulp
  • 19 is a relay valve
  • 20 is a bypass valve
  • 21 is an output shaft
  • 22 is a sun gear rotation sensor
  • 23 is a brake.
  • the pressure sensor, 24 is the vehicle speed sensor
  • 25 is the engine speed sensor
  • 26 is the throttle opening
  • 27 is the controller (TCU).
  • a continuously variable transmission receives a rotational force generated and provided from a power generation device and outputs the torque to a wheel drive device while performing a stepless speed change.
  • a carrier that is connected to the turbine shaft (2) of the power generation means and rotates (revolves) without pinching a number of planetary gear sets, and is assembled so as to freely rotate while being supported by the carrier.
  • a number of planetary gear sets (Sl, S1) formed such that the number of teeth of the planetary gear (S1) on one side of the formed planetary gear set is relatively smaller than the number of teeth of the planetary gear (S2) on the other side.
  • the connection between the turbine shaft (2) of the input stage and the carrier is made by super-line connection, and the first output portion (5, 3) is connected to the planetary gear (S2) having the larger number of teeth.
  • the second output portion (8, 4) includes a ring gear (5) coupled to the outside of the arrangement and rotating, and a forward clutch (3) for regulating a connection between the ring gear and the output stage shaft.
  • the transmission (7, 9) includes a reverse clutch (4), which is engaged inside the arrangement of the planetary gears (S2) and rotates, and the transmission section (7, 9) has a small number of teeth of the planetary gear (S1).
  • a variable speed sun gear (7) coupled to the inside of the array and rotating, and the variable speed sun gear includes a hydraulic motor (9) for providing power to rotate in the same direction as the carrier or to maintain a stopped state.
  • the speed change unit is configured to continuously change the speed between the input / output stages by changing the rotation speed of the hydraulic motor.
  • the hydraulic motor is stopped and the transmission sun gear is maintained in a stopped state, so that the gear teeth between the input / output stages are
  • the main drive torque provided through the turbine shaft (2) of the input stage is set so that the fixed speed is changed according to the number ratio.
  • the sub-drive torque provided through the hydraulic motor (9) is combined through the same stepless variable speed machining process as before, so that the output stage shaft is printed.
  • the variable speed sun gear drive is provided by the rotational force generated in the revolving direction of the planetary gear when the planetary gear transmits the rotational force while revolving and revolving around the variable speed sun gear as a central axis, and the hydraulic motor (9).
  • the sub-drive torque is driven by the sub-drive torque, so that the sub-drive torque is relatively remarkably small compared to the main drive torque to perform the rotation control of the shifting sun gear to achieve continuously variable transmission.
  • the hydraulic motor is not driven by a separate power generation device, but by using the oil pressure of an oil pump (11) of a well-known hydraulic pressure generating and providing device from the power generation device, and to the suction pulp (14) at the oil pump suction port.
  • the oil pressure is discharged from the hydraulic motor (9) so as to be guided to the suction port of the oil pump (11) so as to minimize the power loss.
  • the motor speed is controlled.
  • the electronic control unit senses the pressure in the master cylinder of the power generation device, calculates through the controller (TCU), and increases the reduction ratio in proportion to the sensed pressure. Is controlled to generate
  • FIG. 4 is a graphic diagram comparing operation characteristics between a vehicle transmission according to the present invention and a conventional transmission.
  • the vehicle transmission of the present invention can provide an optimum gear ratio to the vehicle operating conditions and engine output from low speed to high speed running, thereby making the conventional transmission (5-speed operation) possible. It can be seen that not only the fuel saving but also the engine output is improved as compared to the case of).
  • the above-described continuously variable transmission according to the present invention can be applied to all devices required to use the power generated by the main power source by shifting the power depending on the situation. All can be applied to locomotives and ships.
  • the continuously variable transmission system using the gear combination according to the present invention is designed to optimize the engine irrespective of the traveling speed of the vehicle by continuously changing the speed so as to adapt to the traveling state of the vehicle or the like.
  • Improved acceleration performance has an excellent effect of eliminating shift shocks.
  • control operation can be flexibly changed for each vehicle type by changing the program stored in the control unit unit (TCU) of the relevant vehicle regardless of the vehicle manufacturer. Available to duplicate This has the effect of preventing consumption of development costs. At the same time, it has the excellent effect of improving engine output, reducing noise while reducing fuel consumption, and improving gear shifting efficiency through reliable stepless gear shifting by gear combination. is there.
  • TCU control unit unit

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'invention concerne une transmission pour un changement de vitesse continu fiable par engrènement, avec une perte de puissance minimisée, et un dispositif de transmission à variation continue pour véhicules automobiles. Ce dispositif utilise cette transmission pour fournir un rapport de changement de vitesse à variation continue optimal pour un rendement-moteur. Cette invention concerne plus particulièrement un dispositif de transmission à variation continue dual servant à effectuer un second changement de vitesse par l'augmentation ou la réduction d'un rapport de multiplication de sortie, lorsque la vitesse de rotation d'un arbre de turbine est augmentée ou réduite, la vitesse de rotation d'un planétaire de changement de vitesse à sous-entraînement restant inchangée. Un couple réparti étant synthétisé pendant le changement de vitesse et produit, on observe une très faible perte de puissance au niveau de la rotation d'un planétaire à sous-entraînement. Le dispositif décrit ci-dessus est utilisé sur des véhicules automobiles pour un rapport de changement de vitesse précis, flexible et en temps réel. On obtient ce rapport en calculant au moyen d'un contrôleur (unité de contrôle terminal) un rendement moteur, une vitesse de véhicule, un rapport d'ouverture du papillon des gaz, une vitesse de rotation du planétaire à vitesse variable et une pression de freinage. Ledit dispositif est modifié par transformation temporelle et convient parfaitement à toutes les conditions de route et de fonctionnement, de manière à garantir une économie de carburant, un meilleur rendement, un niveau de bruit et d'émission de suies et de fumées réduit et un certain confort de route.
PCT/KR2001/001421 2000-08-22 2001-08-22 Transmission pour un changement de vitesse a variation continue fiable par engrenement et dispositif de transmission a variation continue pour vehicules automobiles utilisant cette transmission WO2002016802A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US10/111,239 US6645106B2 (en) 2000-08-22 2001-08-22 Transmission for performing reliable continuously-variable-speed operation through gear meshing, and vehicle-use continuously-variable transmission device using it
AU2001282633A AU2001282633A1 (en) 2000-08-22 2001-08-22 Sransmission for performing reliable continuously-variable-speed operation through gear meshing, and vehicle-use continuously-variable transmission device usingit

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR10-2000-0048778A KR100374770B1 (ko) 2000-08-22 2000-08-22 기어 치합을 통해 신뢰성 있는 무단 변속 동작을 수행하는 변속기와, 그를 이용한 차량용 무단 변속 장치
KR2000/48778 2000-08-22

Publications (1)

Publication Number Publication Date
WO2002016802A1 true WO2002016802A1 (fr) 2002-02-28

Family

ID=19684581

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR2001/001421 WO2002016802A1 (fr) 2000-08-22 2001-08-22 Transmission pour un changement de vitesse a variation continue fiable par engrenement et dispositif de transmission a variation continue pour vehicules automobiles utilisant cette transmission

Country Status (4)

Country Link
US (1) US6645106B2 (fr)
KR (1) KR100374770B1 (fr)
AU (1) AU2001282633A1 (fr)
WO (1) WO2002016802A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014159839A (ja) * 2013-02-20 2014-09-04 Chuo Univ 遊星歯車装置
CN115332758A (zh) * 2022-09-14 2022-11-11 中国人民解放军海军工程大学 一种用于舰载雷达天线的可升降六自由度平台

Families Citing this family (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2174076C1 (ru) * 2000-02-23 2001-09-27 Коротков Эдуард Константинович Универсальная механическая голономная часть передачи с бесступенчатым изменением крутящего момента (и ее варианты)
CN1291855C (zh) * 2002-12-08 2006-12-27 中国第一汽车集团公司 双电机混合动力汽车动力系统
KR100623082B1 (ko) 2005-04-11 2006-09-14 다이모스(주) 차량용 무단변속장치
US8285431B2 (en) * 2007-11-03 2012-10-09 GM Global Technology Operations LLC Optimal selection of hybrid range state and/or input speed with a blended braking system in a hybrid electric vehicle
ITBO20080577A1 (it) * 2008-09-19 2010-03-20 Cnh Italia Spa Veicolo agricolo a trasmissione variabile continua
WO2013109723A1 (fr) 2012-01-19 2013-07-25 Dana Limited Dispositif de vectorisation de couple d'une transmission à variation continue d'un variateur à bille inclinable
US9541179B2 (en) 2012-02-15 2017-01-10 Dana Limited Transmission and driveline having a tilting ball variator continuously variable transmission
US9556941B2 (en) 2012-09-06 2017-01-31 Dana Limited Transmission having a continuously or infinitely variable variator drive
US9556943B2 (en) 2012-09-07 2017-01-31 Dana Limited IVT based on a ball-type CVP including powersplit paths
US9689477B2 (en) 2012-09-07 2017-06-27 Dana Limited Ball type continuously variable transmission/infinitely variable transmission
JP6247690B2 (ja) 2012-09-07 2017-12-13 デーナ リミテッド 出力連結動力経路を有するボール式ｃｖｔ
WO2014039708A1 (fr) 2012-09-07 2014-03-13 Dana Limited Transmission à variation continue à billes avec mode d'entraînement direct
WO2014039900A1 (fr) 2012-09-07 2014-03-13 Dana Limited Transmission à variation continue du type à billes présentant des chemins de répartition de puissance
WO2014078583A1 (fr) 2012-11-17 2014-05-22 Dana Limited Transmission à variation continue
WO2014124063A1 (fr) 2013-02-08 2014-08-14 Microsoft Corporation Service omniprésent de fourniture de mises à jour spécifiques à des dispositifs
EP2971860A4 (fr) 2013-03-14 2016-12-28 Dana Ltd Transmission à variation continue et entraînement à variateur de transmission à variation continue
JP2016512312A (ja) 2013-03-14 2016-04-25 デーナ リミテッド ボール式連続可変トランスミッション
JP2016520782A (ja) 2013-06-06 2016-07-14 デーナ リミテッド ３モード前輪駆動および後輪駆動連続可変遊星トランスミッション
CN103486202B (zh) * 2013-10-10 2015-09-16 西安创联超声技术有限责任公司 共轴反转行星减速机
US10030751B2 (en) 2013-11-18 2018-07-24 Dana Limited Infinite variable transmission with planetary gear set
WO2015073948A2 (fr) 2013-11-18 2015-05-21 Dana Limited Mécanisme de commande et de détection de pic de couple d'un cvp
US20150142281A1 (en) * 2013-11-18 2015-05-21 Dana Limited Braking management system for a transmission incorporating a cvp
DE102015006084B4 (de) * 2015-05-09 2023-09-28 Renk Gmbh Antriebsanordnung mit einem Überlagerungsgetriebe und einer mit variabel einstellbarer Drehzahl anzutreibenden Arbeitsmaschine
US10024405B2 (en) * 2015-05-12 2018-07-17 Hamilton Sundstrand Corporation Dual redundant linear actuator
US10030594B2 (en) 2015-09-18 2018-07-24 Dana Limited Abuse mode torque limiting control method for a ball-type continuously variable transmission
US10382929B2 (en) * 2016-04-17 2019-08-13 Sonular Ltd. Communication management and communicating between a mobile communication device and another device

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6011750A (ja) * 1983-06-30 1985-01-22 Nec Corp 差動回転装置
JPH109365A (ja) * 1996-06-25 1998-01-13 Kenji Shionoya 無段変速装置
WO1999024736A1 (fr) * 1997-11-06 1999-05-20 Kim, Kil, Hae Transmission a changement de vitesses continu et boite de vitesses pour vehicules utilisant cette transmission

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1530967A (en) * 1924-09-20 1925-03-24 Waterbury Tool Co Power-transmitting device
US2603111A (en) * 1947-06-24 1952-07-15 Madsen Jens Gear device for motorcars
JPS58119122A (ja) 1982-01-08 1983-07-15 株式会社ツ−デン 電気機器兼用の自動ドア用感知板装置
GB8332237D0 (en) * 1983-12-02 1984-01-11 Leyland Vehicles Transmission system
DE3625141A1 (de) * 1986-07-25 1988-02-04 Man Nutzfahrzeuge Gmbh Antriebseinrichtung fuer ein fahrzeug mit notfahraggregat
EP0557700B1 (fr) * 1987-05-12 1995-08-09 Friedrich Prof. Dr.-Ing. Jarchow Boîte de vitesse hydrostatique-mécanique à réglage continu
JPH07127710A (ja) * 1993-05-28 1995-05-16 Friedrich Jarchow 無段油圧変速装置を有する動力シフト歯車装置
DE4343401C2 (de) * 1993-12-18 1995-06-01 Voith Gmbh J M Stufenloses hydrostatisches Leistungsverzweigungsgetriebe
JPH08182710A (ja) 1994-12-28 1996-07-16 Mitsuba Electric Mfg Co Ltd 電動ベッド用駆動モータの制御回路
KR970045324A (ko) 1995-12-27 1997-07-26 김태구 차량의 시동제어 회로
KR19980036378A (ko) 1996-11-18 1998-08-05 김영귀 자동차의 와이퍼장치
KR970058590A (ko) 1997-05-30 1997-08-12 용태웅 계육의 가공방법
US6338689B1 (en) * 2000-06-16 2002-01-15 Sauer-Danfoss Inc. Hydromechanical transmission

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6011750A (ja) * 1983-06-30 1985-01-22 Nec Corp 差動回転装置
JPH109365A (ja) * 1996-06-25 1998-01-13 Kenji Shionoya 無段変速装置
WO1999024736A1 (fr) * 1997-11-06 1999-05-20 Kim, Kil, Hae Transmission a changement de vitesses continu et boite de vitesses pour vehicules utilisant cette transmission

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014159839A (ja) * 2013-02-20 2014-09-04 Chuo Univ 遊星歯車装置
CN115332758A (zh) * 2022-09-14 2022-11-11 中国人民解放军海军工程大学 一种用于舰载雷达天线的可升降六自由度平台
CN115332758B (zh) * 2022-09-14 2024-04-12 中国人民解放军海军工程大学 一种用于舰载雷达天线的可升降六自由度平台

Also Published As

Publication number Publication date
KR100374770B1 (ko) 2003-03-06
AU2001282633A1 (en) 2002-03-04
US20030004030A1 (en) 2003-01-02
US6645106B2 (en) 2003-11-11
KR20020015613A (ko) 2002-02-28

Similar Documents

Publication Publication Date Title
WO2002016802A1 (fr) Transmission pour un changement de vitesse a variation continue fiable par engrenement et dispositif de transmission a variation continue pour vehicules automobiles utilisant cette transmission
AU758770B2 (en) Automatic transmission for vehicles
US7000717B2 (en) Output power split hybrid electric drive system
US7402119B2 (en) Multi-speed transmission for vehicle
KR101853826B1 (ko) 차량 변속기용 제어 장치
KR100524255B1 (ko) 복합 유성 기어 세트 및 이를 갖는 기어 트레인
JPH02130224A (ja) 補機駆動装置
KR100204960B1 (ko) 차량용자동변속기의파워트레인
KR101132753B1 (ko) 유성기어세트 및 이를 이용한 동력 전달 장치
JPH09144835A (ja) 無段変速機
KR19990008220A (ko) 자동차등의 엔진용 고효율 연속가변 트랜스미션장치
JPH0772583B2 (ja) 変速装置
JP2022501559A (ja) 電気自動車用の連続可変トランスミッションを備えたパワートレインおよびかかるパワートレインを操作するための方法
KR100294474B1 (ko) 차량용무단변속장치
KR100301551B1 (ko) 자동차의 기어식 무단변속장치
KR101809257B1 (ko) 차동기어를 이용한 회생제동 하이브리드 변속기 및 이의 작동방법
KR100290244B1 (ko) 무단 변속 장치
KR100286610B1 (ko) 자동차 밸트형무단변속기의 2웨이클러치어셈블리
JPH1182714A (ja) 車両用無段変速機の制御装置
KR970003538B1 (ko) 무단변속장치
KR200189174Y1 (ko) 차량용 무단 변속장치
KR920009578B1 (ko) 차량용 자동 변속기의 1축 5속 변속기구
JP2003094967A (ja) 自動無段連続変速装置
KR100260166B1 (ko) 차량용 무단 변속장치
JPH02159449A (ja) ベルト式変速装置

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BY BZ CA CH CN CO CR CU CZ DE DK DM DZ EC EE ES FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KP KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NO NZ PL PT RO RU SD SE SG SI SK SL TJ TM TR TT TZ UA UG US UZ VN YU ZA ZW

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): GH GM KE LS MW MZ SD SL SZ TZ UG ZW AM AZ BY KG KZ MD RU TJ TM AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG

ENP Entry into the national phase

Ref country code: JP

Ref document number: 2002 521862

Kind code of ref document: A

Format of ref document f/p: F

WWE Wipo information: entry into national phase

Ref document number: 10111239

Country of ref document: US

121 Ep: the epo has been informed by wipo that ep was designated in this application
REG Reference to national code

Ref country code: DE

Ref legal event code: 8642

122 Ep: pct application non-entry in european phase